Rotary kinetic fluid motors or pumps – Selectively adjustable vane or working fluid control means – Upstream of runner
Reexamination Certificate
2001-04-04
2003-04-15
Look, Edward K. (Department: 3745)
Rotary kinetic fluid motors or pumps
Selectively adjustable vane or working fluid control means
Upstream of runner
Reexamination Certificate
active
06547521
ABSTRACT:
BACKGROUND OF THE INVENTION
1. Field of the Invention
The invention relates to an axial flow machine, in particular a turbine with a guide apparatus in the flow duct, which guide apparatus comprises a row of adjustable guide varies and is bounded, on the one hand, by an inner hub and, on the other hand, by an outer guide vane carrier, the guide vanes being, on the one hand, rotationally supported in radial bearing holes of the annular guide vane carrier and, on the other hand, the tip profile of the guide vanes sealing against the guide vane carrier and the root profile of the guide vanes sealing against the hub, i.e. the guide vanes are supported at one end.
2. Description of the Related Art
Adjustable, in particular turbine, guide apparatus is, as is known, employed in turbine and turbocharger construction in order to permit better matching of the turbine to the particular operating conditions occurring during operation. This is because, in the case of an exhaust gas turbocharger, for example, the characteristics specified, in association with a piston machine of high specific power, make it difficult to make the desired air quantity available over the whole of the operating range. By adjustment of the guide apparatus cross section, the boost pressure, and therefore the air quantity available, for a given load point can therefore be modified within certain limits. By opening the turbine cross section with increasing load, in accordance with a specified characteristic, the increase in pressure can then be limited in such a way that, at full load, the scavenging air pressure, and therefore also the ignition pressure and the fuel consumption, are set to those for the normally designed engine.
The efficiency of the turbine with an adjustable turbine guide apparatus can therefore also be raised or lowered, particularly in the case of operation away from the design point.
Adjustable turbine guide apparatus usually have a plurality of guide vanes which are rotatably arranged about an axis and which can be connected in an articulated manner by means of levers and setting rings.
A fundamental distinction must be drawn between adjustable turbine guide apparatus for axial and radial flow turbines. Whereas the radial flow adjustable turbine guide apparatus can be of relatively simple construction (see, for example DE 42 18 229 C1), it is essentially more complicated to realize the axial flow arrangement because the hub and inlet casing contours, in particular, must be designed to be spherical, i.e. at least curved. This is necessary in order to generate a uniform radial gap relative to the hub and inlet casing contours at all guide vane settings.
DE 42 13 709 A1 reveals an axial flow machine of the generic type, in particular an axial flow turbine. In this case, the adjustable turbine guide apparatus offers the possibility of reducing the flow cross section in the turbine at part load of the engine by rotating the guide vanes and, by this means, of raising the air pressure before the cylinder.
The previously known axial flow, adjustable turbine guide apparatus comprises, within the walls bounding the annular flow duct, the inner hub, on the one hand, and, on the other hand, the outer guide vane carrier which encircles the hub as an annulus. This guide vane carrier is secured in the inlet casing of the turbine. The actual adjustment of the guide vane takes place by means of a linkage lever and, preferably, automatically as a function of the operating parameters such as supercharge pressure, rotational speed, etc.
In order to keep the flow losses in an axial flow, adjustable turbine guide apparatus, the gaps between the guide vanes and the inlet casing, and/or the hub, must be kept as small as possible. Various measures have already become known for this purpose, such as the guide vanes having a rotary trunnion, which is supported in the guide vane carrier and a vane rotary plate which is sealed relative to the inlet casing (see, for example, DE 27 40 192 C2 or DE 42 37 031 C1).
On the other hand, and so that the guide vanes do not jam during “hot” operation, they must usually be installed with appropriate clearance. So that easy adjustment can also be ensured in the case of load changes, i.e. in the case of differential thermal expansion between the components of the guide apparatus, sufficiently large gaps have previously been accepted but these, i.c. the resulting gap flows at the tip and at the root of the guide vanes, can greatly perturbate the main flow in the duct.
These two requirements for, on the one hand, minimizing the gap cross sections and, on the other hand, easy adjustability of the components, are mutually contradictory and, for this reason, the adjustable, axial flow turbine guide apparatus realized in the past were either running easily or had small flow losses.
SUMMARY OF THE INVENTION
The invention is based on the object of developing an axial flow machine of the type mentioned at the beginning in such a way that the components of the guide apparatus are both easily actuated and permit only small gap flows. It is, therefore, required to combine both the requirements quoted above in a new axial flow machine.
The object is achieved by the provision in an axial flow machine such as a turbine, of guide apparatus in the flow duct. This apparatus comprises a row of adjustable guide vanes, these being bounded at one end by an inner hub and at an opposite end by an outer guide vane carrier. The guide vanes are rotatably received in and flexably supported in radial bearing holes in the vane carrier. The vanes each have a tip profile and a root profile, the guide vane tip profiles sealing against an inner contour of the vane carrier, and the root profiles sealing against a flexible contour part of the inner hub.
Because, at least in the sealing region at the root profile of the guide vanes, the hub is embodied with a flexible hub contour and the single-end support of the guide vanes in the guide vane carrier in the direction of the guide vane axes likewise has a flexible configuration, the flow losses through gaps between the guide vane contours and the inlet casing and hub contours can be reduced and, in addition, stressing of the components of the adjustable guide apparatus, caused by sealing elements and by thermal expansion of the components, is avoided.
The fact that the flexible configuration of the support for the guide vanes in the guide vane carrier by means of a spring acting, in each case, in the direction of the guide vane axes, in particular a plate spring is achieved in a particularly advantageous manner ensures that the tip profile of a guide vane is in contact with the inlet casing contour in each operating condition, by which means the gap between these two components can be kept very small or can be avoided altogether.
Because the flexible hub contour is embodied, in an advantageous manner, in the form of an inner ring, which is fitted into the hub contour and which is supported, in the preloaded condition, against the root profiles of the guide vanes, this inner ring is always in contact with the guide vane contours.
In a preferred embodiment, furthermore, the inner ring is provided with a slot for assembly so that, here again, it is possible to compensate for thermal expansion. The slot is arranged in such away that it is located between two guide vanes such that a guide vane movement during an adjustment procedure bypasses said slot, so that the losses caused by the slot can be minimized.
Because, in addition, the slot is covered, relative to the hub internal space, by means of a sealing plate, which isolates a communication between a hub internal space and the flow duct, mass flow losses through the slot can be avoided.
In a preferred embodiment, the inner ring is flanged onto the hub in such a way that it can be moved in the radial direction of the inlet flow casing, i.e. in the direction of the guide vane axis, but is inserted into the hub contour with only small clearance in the axial direction of the inlet flow casing so there is no substantial moveme
Bartholomä Klaus
Schrott Karl Heinz
Cohen & Pontani, Lieberman & Pavane
Edgar Richard A.
Look Edward K.
MAN B&W Diesel Aktiengesellschaft
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